Governing mechanism for turbines.



A TTORNE Y.

PATENTBD AUG. 9,1904. J'. WILKINSON. GOVBRNING MBCHANISM POR TURBINBS.

3 SHEETB--BHEET 1.

No MODEL! A PPLIUATION FILED un. a, 1904.

lll. llllllll I.

WITNESSES.- l M f6.

No. 766,921. PATENTED AUG. 9, 1904. J. WILKINSON. v GOVERNING MECHANISM FUR TURBINES APPLICATION FILED APB. B, 1904. N0 MODEL.

3 SHEETS-SHEET 2.

WITNESSES. 'INI/ENTo/e No. '166,921t PATBNTED AUG. 9, 1904.

J. W1; SON.

GOVERNING MECH ISM FOR TURBINES.

APPLICATION FILED APR. B, 1904. OOOOOO L. 3 EHEETS-SHBET 3A Jaaa.

llniiTnn STaTns JAMES XVTLKINSON, OF

BIRMlNGllAb/l,

.Patented August 9, 1904i.

ALABABIIA, ASSIGNOR TO THE VILKINSON STEAM TURBTNE `OOMPAISI'Y, OF BIRMTNGHAM, ALABAMA,

TA CORPORATION OF ALABAMA.

GOVEFTNING MECl-lrlliNlSNl FOR TUHBINES.

SPECIFICATION forming part of Letters @attent No. 766,921, dated August 9, 1'904.

Application filed April 8, 1904. Serial No. 202,245. (No model.)

To all whom t may conce/vt:

Be it known that 1, JAMES WILKINSON, a citizen of the United States, residing at Birmingham, in the county of Jefferson and State of 5 Alabama,have invented new and useful lmprovements in Governing l\/I.echanism for Turbines, of 'which the following is a specification.

My invention relates to improvements in elastic-Huid turbines of the impact and the re- Io action type, and has for its object to perfect a controller mechanism for the supply of motor 'fluid which will enable the turbine to operate with high eiiiciency under normal load variations and at the same time avoid the serious I5 loss in economy which attends the operation of the present turbines under an overload. The additional motor fluid required to drive the turbine when itsload is greater than can be carried by the full normal supply of preszo sure has heretofore been introduced into a low-pressure stage in multiple-stage impactturbines and at an intermediate point in the working passage of reaction-turbines. This practice is attended by two serious objections,

first of which is that the introduction of the highly-heated motor fluid into the turbine at a point where the active lluid therein will have given out most of its heat and be at a low temperature causes an excessive initial condensa- 3o tion,the water of which not only represents loss of energy, but also constitutes a serious detriment in that it creates friction and is difficult to dispose of. The other objection is that by .introducing the overload supply at an inter- 5 5 mediate point in the working passage of either type of turbine but a fraction of its energy of pressure will be converted into velocity,

. for the succeeding vanes are not designed nor intended to abstract all of the velocity from 4o the motor fluid. To obviate these objections in connection with multiple-stage impact-turbines and reaction-turbines having relatively short working passages, l provide a plurality of overload-nozzles leading through the supply-head and provide valves therefor which are controlled and operated from th-c governor for the normal-load valves.- ln this manner when the load becomes excessive all the overload-valves are intermittently opened and admit the additional supply of motor lfluid to the lirst stage. Since this supply will be greater than that which can normally flow 'through the second-stage nozzles of an'impact-turbine,` the lirst stage will practically constitute a sup- ]jily-ehamber for the second stage, which thus becomes the lirst. lhough this may have a tendencyT to decrease the elliciency of the turbine by shortening its working passage, the loss resulting therefrom will be small compared with the present practice. 1n reactionturbines having' short working passages the effect of this increased initial supply will be to move the maximum temperature-line forward in the working passage, practically shortening its length. i

Myinvention further embodies material improvements in governing the normal fluidsupply by providing' means to vary by hand the area of the working passage, so that when' operating at constant underloads the eil'ective 70 power of the turbine is proportionately reduced and it operates as at its full load, which representshighest efficiency. Thus l provide hand-operated stage-valves in combination with governcr-controlled su pply-valves, any number of which 0may be locked in a closed position to correspond with the stage-valves set closed.

My invention further relates to improvements in a governing mechanism for the nor- 8O mal and overload sul'iply-valves and which controls fluid-pressure means to pulsate the supply-valves according to the principles set forth in my prior patents lrelating to pulsatory governor means.

The details of construction embodying my invention and which are hereinafter more fully described are illustrated in the accompanying drawings, forming a part hereof, and in which# Figure l is a side elevation of my improved turbine and governor operating an electric` dynamo. Vg. 2 is a partial transverse sectional view illustrating one of the supplyvalves and itsl operating means disposed in the supply-head. Fig. 3 is a partial end view of the supply-head, illustrating a row of valves and the conduits leading thereto from the iluid-pressure-controller means. Fig. 4 is a sectional view along' the line a a', Fig. 3, and illustrating the controller-nozzle. Figs. 5 and 6 are side and end views of the governorcam. Fig. 7 is a sectional view through a group otl working' passages leading across the stages and shows the overload-valves closed and a row of normal-load valves across stages also closed. Fig'. 8 is a sectional view along the line y y, Fig. 3. Fig. 9 is a broken-away view illustrating means for simultaneously opening' all the supply-valves. Fig. 10 is an enlarged detail view of the indicator on the operating-stem for a stage-valve.

I have illustrated my invention as applied to a multiple-stage impact-turbine mounted upon a bed-plate 1 and acting to drive a dynamo 2 by means of a main shaft 3, suitably supported in bearings 4, which, with the dynamo, arealso bolted to the bed-plate. The turbine comprises an outer shell 5, which surrounds the inner casing formed by the supply-head 6 and diaphragm-partitions 7, interposed between said supply-head and the eX- haust or condenser casing 8. The exhaustpassage casing is securely bolted or otherwise connected to the shell 5, which is provided with a channel 9 around its end adjacent to the suppl y-head 6. The supply-head and succeeding diaphragms are provided with interlocking iianges 10 and 11, respectively, which constitute the side walls 'ot' the compartments within which -the wheels 12 rotate. The wheels are keyed to shaft 3 and are disposed one in each compartment and provided with a peripheral row of concave-convex buckets 13, secured to or formed integral with their rims 14. Segmental rings 15 are disposed around the inner walls ot' these several compartments and are provided with inwardlydisposed heat-radiating projections 16. A

locking-ring 17 engages within the channel' 9 in the shell and is provided with a flange 18, which engages the tcp surface of the supply-head 6 and serves as an abutment to hold the turbine-sections together against displacement by interior pressure. I provide a nozzle-strip 19,` which is securely bolted to the inner face of the supply-head 6 and is provided with a plurality otl nozzlepassages 29, leading' at an incline therethrough and disposed to deliver motor fluid against the rotating buckets 13. This ring may be formed in segments and secured to the head by capscrews 21, as seen in Fig. 2. Motor-Huid pressure is admitted to an annular chamber 22, formed between the shell 1 and the turbinecasing, through a port 23. (Shown in dotted lines, Fig. 1.) A gate-valve operated by wheel 24 controls this supply. Branch passages 25 lead from chamber 22 through the supply-head 6 and through ports 26 admit the motor-fluid pressure to each of the nozzle-passages 20.

A beveled puppet-valve 27 engages a seat 28 at the inlet end of each port 26 and acts under the control of a piston 29 to -admit or cut OH? motor fluid from a nozzle 20. I provide a plurality of chambers in the supplyhead and seat therein blocks 30, formed with a chamber 31, serving as a cylinder for the piston 29, which operates the valve 27 by means ot` a hollow stem 32, leading through a suitably-packed opening in block 30 and through the passage 25. Screw-plugs 33, screwed into the openl ends of chambers in the head, form the outer ends ot the cylinders 31. The pistons 29 are preferably beveled at each end, and the ends of the cylinders are correspondingly beveled. lIotor-iuid pressure after acting against therotating buckets 13 in the lirst wheel-compartment will be discharged against the buckets in the second and succeeding wheel-compartments through stage-nozzle passages 34, leading transversely through the diaphragm-partitions 7 and provided with rotary valves 35. These valves, seated in chambers formed in said diaphragms, are disposed at the contracted or inlet portion of the nozzle proper. Enlarged openings 36 constitute the supply-openings in the diaphragms for the nozzles 34. Plugs 37 (shown in dotted lines, Fig. 8) close the outer ends of these valve-chambers, which are preferably bored into the diaphragms from their outer peripheries, and operating-stems 38 for the stagevalves lead through these plugs and across the supply-chamber 22 and through the shell 1. The outer ends of the stems 38 are disposed in the recessed end of a packing-gland 39. seated in shell 1 and acting to prevent the escape of motor-fluid pressure from chamber 22 around stems 38. I secure an indicator 40 to the squared end of each of these stems and pro-v vide suitable marks representing an open or closed position for the valve 35, so that by means of these indicators the position of the stage-valve can be immediately determined. It will thus be evident that it is my intention to control the stage-valves 35 manually and independently of the supply-valves, which, it will be noted in Fig. 7, are double in number tothe stage-valves in each diaphragm.

My governor controlled fluid pressure means for actuating the supply-valves 27 constitutes an improvement upon controlling mechanism which is shown and the operation of which is fully described in my Letters Patent No. 753,773 and which, briefly described, comprises a controller-chamber 41, formed in a plug 42, inserted in the supply-head and disposed beneath the flange 18 of the ring 17. Fluid-pressure is admitted to chamber 41 through a passage 43, leading from the chamber 22 through the head -and entering a cylinder 44, in which a governor-actuated controller-piston 45 moves pressure-tight. A curved nozzle-passage 46 leads through this piston and discharges the motor-fluid pressure from' IOO IIO

the cylinder44 into a normally open exhaust` passage47, leading' through the head, and a suitable nozzle 48 'in the ring 19. All of the controller fluid will be directed by the nozzle 46 when in its loweijposition into this passage 47; but when the nozzle is raised by means of stein 49. this nozzle portion will come opposite to one or both of the c ntrollerpas sages 50 and 51, which are divided hy a thin partition 52 from each other and disposed in vertical alinement with the passage 47. The passage 50 at its inlet end is separated from the passage 47 by a thin division wall 53,

. formed integral in the plug 52, through which sages, Fig. 2, which constitute continuations of the controller-passages 50 and 51 and are so indicated. From the passage 5() branch passages 56 lead transversely through the head and plugs 33 and enter the upper ends of alternate cylinders 31 of the series. spending passages 57 lead from the controllerpassage 51 and enter the upper ends of the cylinders 31, which are not in communication with the passages 56. When the nozzle46 is disposed opposite to the passage 5() the stream of controller Huid will be discharged therein, and since no outlet is -provided for the Huid admitted thereto this stream will by impact raise the pressure throughout the passage vand in the alternate cylinders 31, which are in communication therewith, until the pressure above pistons 29 is substantially that of the motor- 'luid pressure. l/Vhen this is the case, the pistons will move downwardly toward their valve-closed7 position, for it is my purpose to admit a relatively lower pressure from a` stage to the lower ends of all the cylinders 31 by means of an annular passage 58, formed by a grooved strip 59,inserted in an annular channel in the head communicating with the `several cylinders by branch passages 60 and with a stage-pressure by a passage 61, formed by a grooved strip 62, disposed in a channel lead- Fing across the supply-head and diaphragm to Gorrejust described in connection with the operation of the pressure in passage 50.

It will be seen that I have divided the supply-valves into two independent groups, the valves in each of which will be simultaneously opened or closed, according' to the pressure existing in the passage which controls their action; The valves controlled by the passage 51, which l shall hereinafter refer to as the normal-load valves, will admit when held constantly open sullicient motor-Huid pressure to drive the turbine with the highest efiiciency under its full load. As the load decreases I proportion the supply of motor iiuid thereto by pulsating' the` valves, so that they vary the total volume of the motor fluid delivered without effecting' its velocity. In previens patents 1 have shown and described various means for pulsating the motor fluid so that by interrupting its flow .for periods of varying duration its volume will be directly proportioned to the load. My present governing mechanism comprises a governor 64, mounted on a counter-shaft 65, driven' from shaft 3 through suitable speed-reducing' gears disposed within the casing66, forming a part of one of the shaft-bearings 4. A standard 67 is mounted on the top of easing 66 and forms at its lower end a bearing for shaft and at its upper end a horizontal'bearingfor the stem 49', which actuates the controllernozzle 46. This stem passes through an extension 68 of the plug' 42, which is disposed in an elongated opening' 69 in the flange 18 of the locking-ring 17. A screw-tap 70 en* gages this extension 68, which holds suitable packing around the stein to prevent'leakag'e of pressure from chamber 41. The stem 41 is bifurcated at its outer end, and a roller 71 is `rotatably mounted on. an axis 72 therein. This roller is disposed to engage a controller cam 73, feathered to shaft 65, from which it receives rotary motion, and suitably connected to the governor 64, by means of which it vertically shifted. r1`his cam, which is shown .in detail in Fig. 5, is eccentrically shouldered at 74. This shoulder commences at a point near the cylindrical end 75 of the cam and leads in a spiral completely around the cam` to form a helical shoulder 76. A similar shoulder 77 encircles the outer end of the cam,

IOO

leaving' a cylindrical path 78 between the Y which by means of this roller 7l engages this cam, can assume three stationary positions. When operating on path 75, the nozzle 46 will be opposite passages 50 and 51 and discharging' its pressure directly thereinto will main-` tain all` of the valves 27 closed. NVhen opvalves controlled by passages 5l will be held open and all of the overload-valves held closed by the controller-stream, which is directed -partly into passages 50 and 47 and by its ejector action exhausts the pressure from passage l, and when 'operating on path 8l nozzle 46 will be directly opposite to ejector-passage 47 and will exhaust the pressure from passages 50 and 51 to maintain all of the normal and overload valves open. Then controlling the normal-load valves, the governor will shift the collar 73 so that the roller 7l moves between the cylindrical paths 75 and 78, when it will engage the straight edge 8O of the shoulder 74 and ride on said shoulder for periods of varying duration, according to its position relative to the spiral of shoulder 76. Then riding on this shoulder, nozzle 46 will inject pressure into passage 5l to close the normal-supply valves, and when off the shoulder the nozzle will eject pressure. from said passage and cause said valves to open. At full load the nozzle is stationary, since roller 7l will be riding on path 78. If now the load become excessive, the governor will lower cam 73 until the roller begins to engage the helical shoulder 77, when the nozzle 46 will commence to intermittently exhaust pressure from passage 50 and permit the overload-valves to pulsate. The load Vif it increases will cause the cam 73 to move downwardly until roller 7l ultimately rides on path 81, when all supply-valves are open. I thus provide means to compensate all intermediate variations of load, and they will operate successfully when the load is uncertain and varies largely.

It must be evident, though, that the highest efliciency in operation exists when the roller rides on path 78, since the liow of Huid is then directly proportioned to the load and uninterrupted; and it is my object to provide means to keep the turbine at its highest eflciency when running under a constant load less than its full power. This would be the case where a constant load required but half of the horsepower capacity of the turbine, and where without my present" improvements the normal load supply valves would be opened and closed for equal intervals by the governor. If the capacity of the turbine be reduced by half, the governor would then act as at full load and the roller 7l would ride on path 78. I fractionalize the capacity of the turbine by providing a device to lock each supplyvalve in a closed position independently of the governing means, which device comprises a screw-rod 82, leading through a central screw-threaded opening 83 through plug 33 and its extension 84, constituting a packinggland similar to 68 and operated by a wheel 85 on its outer end. Its inner end is enlarged at 86 and forms a piston, which is disposed in a cylinder 87, formed in piston 28 and stem 32 and acts as a dash-pot to reduce the suddenness of the valves movements. This' rod can be screwed down until. its end engages the inner end of cylinder 87, when the valve will be held firmly closed. This same construction applies to each supply-valve, and therefore when it is desired to reduce the capacity of the turbine I screw down any desirable number of supply-valves and by hand close the corresponding stage-valves in the line of the fluids How across stages, which reduces the total area of working passage and accordingly the capacity. At the same time it does not affect the governors control of the other `supply-valves` which are slightly pulsated or held constantly open, according to the accuracy with which the capacity of the turbine is proportioned to the load.

By having the stage-valves hand-controlled it is possible to adjust them to produce a great variety of effects, which will enable me to adapt the turbine to any use. I may also set the supply-valves to open any desired distance by moving the piston 86 inwardly to act as a stop.

In Fig. 9 I illustrate means for simultaneously opening all the valves 27 for starting the turbine and blowing out all water of condensation, which comprise a passage 88, leading from the upper end of chamber 22 to a chamber in head l, which opens into a passage 89, leading through the grooved strip 59 and entering the annular passage for admitting stage-pressure below valves 27. A valve 90, having a screw-threaded body portion which engages threads cut in the inner wall of its chamber, normally closes passage 89; but it may be opened by turning stem 91, connected to valve 90, and extending outwardly through casing l and a packing-gland 92. Then this valve is unseated, the motor-fluid-supply pressure rushes through passages 89 60, opening the supply-valves by admitting a high pressure beneath them, and thus causing at once a full flow of pressure through the turbine. A part of this pressure from passage 89 will escape into the first stage through passages 6l and 63. f

Though I have shown stagepressure used to open the supply-valves, I may substitute therefor pressure from chamber 22, in which case I can readily secure the same differential in the pressure el'ects by increasing the size of stem 32 or otherwise reducing the area of pistons 29 exposed to the lower pressure to unbalance them.

By normal-load-supply valves I refer to any desired number of valves controlling the admission of motor fluid to supply nozzle passages whose combined cross-sectional area is adapted to admit a volume of motor fluid suiiicient to drive the turbine under its approximate full-load capacity, and they may accordingly be referred to as the full-loadsupply valves and nozzles as contrasted with IOO IIO

the overload-supply valves and nozzles which control the admission of motor fluid when the 'load has exceeded the approximate lull-load capacity ol""the turbine. In this connection and a compound 4overload nozzle, and in the same manner the construction et the valves may be varied and the manner of grouping changed Without departing from my invention.

Having thus described my invention, what I claim as new, and desire to secure by Letters Patent, is#- 1. In a turbine, a plurality olE {luid-actuated supply-valves which control the admission ol motor Afluid to nozzle-passages, a controllernozzle for said valves, and a governor-shifted cam for oscillating said nozzle to pulsate said valves.

2. In a turbine, a plurality of full-load-su plply valves, a passage for conducting an actuating lluid to the valves oit' said group, in combination with a group of overloadsupply valves, a passage conducting actuating lluid 'to the valves of said group, and governor means to pulsate the pressure admitted to one ol" said passages While maintaining the other mit a volume of inotor fluid suliicient to drive the turbine at said full load,and a governorcontroller means to vary the volume ot' l'luid admittedby said nozzles, in combination with a group oi' nozzles designed to admit motor lluid only when the load exceeds the full-load capacity, and means to pulsate the valves ol2 said latter' group to vary the overload-su'mnly of motor liuid in proportion to the, overload, While the full-load valves are maintained open.

5. A governing means 'l'or elastic-lluid turbines comprisinga plurality of valves, governor-controlled means to simultaneously pulsate said valves to vary the volume ol" fluid admitted in proportion to the load, and means to cut one or more oi said valves out oi service to increase the duration of thefii'npulses ol. fluid-pressure delivered by the active governor-controlled valves during a substantially constant underload.

6. In a governing' means lor elastic-il uid turbines, governor-controlled means to admita `the construction ot' the several nozzle-passages and or the valves may be varied, and they may 'be iormed as parts oi a compound lull-load pulsatory supply oill motor-lhiid pressure to the turbine and to vary the duration of the impulses, .in comliiinaticm with means l'or reducing the cross-sectional area of the stream oi' goverrier-controlled motor liluid to maintain the impulses of fluid-pressure utilized to drive the turbine or' maximum duration.

7. In a governing means `toi" elastic-Huid turbines, governor-controlled means to admit a pulsatory supply ol" overload motorfluid pressure, in combination with a constant snpply oli' full-load fluid-pressure when the turbine is operating' under an overload, and means for reducing' the cross-sectional area of Ithe stream ol overload motor lluid ,to maintain the impulses of maximum duration.

8. In a governing means for turbines, a plurality of fluid-actuated supply-valves which are controlled in two groups, a fluid-controller passage for each group and a governorcontrolled means which diverts a 'freely-flowing stream oi" l'lnid into one ot' said passages intermittently, and into the other constantly when the turbine .is operating' under a ,fraction of its full load.. 9. In a governing means for turbines, a plurality of fluid-actuated supply-valves which are controlled in two groups, a fluid-controller passage 't'or each group, a governor-controlled means which diverte a freely-flowing stream of l'luid into one of said passages intermittently and by an ejector action exhausts the pressure :from the other passage whenthe turbine is operating under a fractional overload.

l0. In a turbine, a group ol fluid-controlled full-load-supply valves, la group of {luid-controlled overload-supljily valves,` and a linidpressure-governing means comprising' a controller device, a l[luid-conduit leading to the several valves of each group, and a controllercam which under a maximum load moves said device ,to a point Where a lrecly Flowing stream under its control will operate by an ejector action to exhaust the pressure from said. conduits and cause 4the valves oit' both groups to open.

11. In an elastic-Huid turbine, one or more nozzle-passages delivering motor l'luid against a rotating element, one or more reciprocating supply-valves therefor, each olf said valves having a chamber formed in a portion movable therewith, and means to dash-pot the action of said valves comprising an adjustable rod for each valve adapted to enterthe chains ber movable with said valve and act as the piston ol. a dash-pot to retard said valves movements.

12. In a turbine, a rotating' element, an induction-nozzle discharging` [luid -pressure against said element, a reciprocating motorflluid valve therefor, and alluid dash-pot there- IOO IlO

for comprising a cylinder movable with said valve, and an adjustable piston therein. A 13. In a turbine, a plurality of full-loadsupply valves controlling the admission of motor fluid to nozzle-passages, governor-controlled means to pulsate said valves simultaneously to vary the total volume of motor fluid without affecting its velocity.

14. In a multiple-stage turbine wherein the motor fluid is fractionally converted into velocity,valves controlling the supply of motor Huid, governor-controlled means to intermittently actuate said valves under fractional loads to pulsate the supply ofV motor iuid, and rotary manually-operated valves for controlling the flow of fluid between stages.

l5. In a multiple-stage turbine, supply and stage nozzle passages for discharging motor fluid against rotating elements, fluid-actuated valves pulsating the flow of fiuid through the supply-passages, and manually-controlled valves between stages.

16. In a turbine, a plurality of nozzle-passages admitting a supply of motor fluid calculated to operate, the turbine under full load, in combination with a plurality of overloadsupply passages, valves therefor and a governor means to pulsate said valves.

17. In a turbine, a plurality of nozzle-supply passages admitting motor fluid,valves for said passages which are controlled in two separate groups, the valves and nozzles of one group being adapted to admit a suliicient volume of motor fluid to drive the turbine under loads not exceeding its full-load capacity, said other valves and nozzles being' adapted to admit a supply of motor Huid to operate the turbine under overloads, and means to control the groups of valves separately.

18. Inaturbine, aplurality of full-load-supply valves controlled simultaneously in a group, a plurality of overload-supply valves simultaneously controlled in an independent group, and governor-controlled means to pulsate the valves of one or the other of said groups when the load is above or below the turbines full-load capacity.

19. In a turbine, a plurality of supply-valves which admit a volume of fluid-pressure sulficient to drive the turbine under full or fractional loads, in combination with one or more nozzle-passages for admitting fluid-pressure to drive the turbine under overloads, and

means to pulsate the overload supply of fluidpressure admitted by said nozzles.

20. In aturbine, one or more overload-supply passages, means to normally close said passages, and governor-controlled means to intermittently open said passages to admit a pulsating supply of overload fluid-pressure which varies in volume but not in velocity.

2l. In a turbine, a group of full-load-supply passages and valves therefor, an independent group of overload-supply passages and valves therefor, in combination with a governing means which pulsates said group of full-load-supply valves under a fractional load, maintains them open under full and excessive loads, and pulsates said group of/overloadvalves only when the load is excessive.

22. In a governing means for an elasticfluid turbine wherein the motor fiuid'issuccessively discharged against rotating elements, the combination of governor-controlled supply-valves all of which move simultaneously, with one or more independentlyoperated valves between rotating elements.

23. In a multiple-'stage turbine, supply and stage valves, governor-controlled means to pulsate the motor Huid admitted by the supply valve or valves, and manual means to operate said stage-valves.

24. Ina multiple-stage turbine, a supplyvalve for the admission of motor fiuid and means to pulsate it to vary the volume of the fluid without affecting its velocity, in combination with a stage-valve which is independently controlled.

25. In a multiple-stage turbine, a plurality `of supply-valves for the admission of motor iiuid capable of driving the turbine under an approximate full load, governor-controlled means to pulsate them simultaneously, in combination with a plurality of manuallyoperated valves between stages.

26. `In a multiple-stage turbine, the combination of a plurality of full-load-supply valves for the admission of motor fluid to the first stage, governor-controlled means to open and close and to pulsate all saidvalves simultaneously, and independent manually-controlled valves between stages.

27. In aturbine wherein the velocity of the motor fluid is abstracted by succeeding rows of rotating buckets, the combination of passages for discharging a full-load supply yof motor fluid against the first row of buckets, governor-controlled valves for said passages which are simultaneously pulsated until the turbine is under a full load when they are held open, passages for Adischarging motor fluid against succeeding rows of buckets and independent manually-controlled valves for said passages.

28. In a turbine, a plurality of passages for discharging motor fiuid against a rotating element, valves for said passages, motors to actuate said valves, and governor controlled means .to intermittently energize all said motors to pulsate the motor-fluid supply without varying its velocity when the turbine is operating at less than full load, and which maintains said valves open under full load.

29. In a turbine, a plurality of full-load-supply valves, and a governor-actuated device to control fluid-pressure to simultaneously pulsate all said valves by definitely opening and closing them for periods of varying duration to vary the volume but Inot the velocity of the motor fluid.

30. In a turbine, a plurality of nozzle-passages, fiuid-pressure-controlled valves there- IOO IIO

all of said valves, andfgovernor means to intermittently admit pressure t0 said conduit and pulsate said valves simultaneously until the turbine is under a full load when said valves are maintained constantly open.

32. In a multiple-stage turbine, a plurality of full-load-supply valves controlling the admission of motor `Huid to the `first compartment, aplurality of stage-valves controlling the discharge of motor fluid into a succeeding stage or wheel compartment and corresponding in number with said supply valves, in combination with one or more overload-valves contrblling the admission of an extra supply of motor fluid to said lirst stage.

33. In a multiple-stage turbine, nozzle-pasages for admitting motor liuid to the several stages, the nozzle-passages for the first stage being greater :in number than the passages which discharge the motor Huid therefrom into the succeeding stage, the excess number of supply-nozzle passages being adapted to admit an overload-supply of motor iiuid.

34s. In a multiple-stage turbine, a plurality of working passages for the motor fluid leading across the stages and comprising supply and stage nozzle passages and interposed rows of rotating buckets, in combination with one or more overload-supply nozzles for the lirst stage only.

35. In aturbine of the jet type wherein the motor fluid is discharged against rotating elements in successive compartments, conduits connecting said compartments, and passages for admitting motor fluid to the lirst compartment which equal or exceed in cross-sectional area the conduits leading' therefrom to provide for the admission of an overloadsupply of motor fluid to the lirst stage.

36. In a multiple-stage impactturbine, means to drive the turbine under full or fractional loads comprising' one or more supplyvalves for each stage which increase in crosssectional area, in combination with one or more auxiliary overload-supplyVvalves which control the admission of an overload-supply of motor fluid to a high-pressure, as contradistinguished from a low-pressure stage.

87. In a multiple-stage turbine, a plurality of supply-valves for the lirst stage, a part of which constitute normally closed overloadvalves, means to open said overload-valves to admit an overload-supply of motor fluid to the lirst stage whereby the effective working passage of the motor [luid is shortened and the velocity of the motor-fluid supply to the succeeding' stages increased.

In a multiple-stage turbine, a plurality of valves between stages, a `corresponding number of supply-valves for the lirst stage, and an independent group of overload-supply Valves interposed among said supply-valves.

39. In a turbine operating' by stage eXpansion, supply and stage valves, a governing means for the supply-valves, in combination with means to set both supply and stage valves so that the capacity of the turbine may be varied without interferingwith lthe action of thejgoverning means.

40. -In an elastic-fluid turbine, a plurality of governor-controlled supply-valves, governor-controlled means to open and close said valves, in, combination with manually-controlled means to lock any or all of said governor-controlled valves in their closed position.

` 4:1. In an elastic-fluid turbine, the combination of a plurality of supply-valves, governorcontrolled means to operate said valves, a chamber carried by each of said valves, and a plurality of screw-rods adjustably mounted in a stationary element of the turbine and adapted to enter said chambers and engage said valves to hold them closed and to dashpot their action when they are opening and closing subject to the control of a governor means.

In testimony whereof I have signed my name to this specilieation in the presence of two subscribing witnesses.

JAMES IILKINSON.

Witnesses lil. M. llon'roN R. I). JOHNSTON. 

